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WO1994027031A1 - Systeme mecanique de transmission de puissance pour ailettes rotatives - Google Patents

Systeme mecanique de transmission de puissance pour ailettes rotatives Download PDF

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Publication number
WO1994027031A1
WO1994027031A1 PCT/US1994/005464 US9405464W WO9427031A1 WO 1994027031 A1 WO1994027031 A1 WO 1994027031A1 US 9405464 W US9405464 W US 9405464W WO 9427031 A1 WO9427031 A1 WO 9427031A1
Authority
WO
WIPO (PCT)
Prior art keywords
vanes
cavity
chamber
hub plate
vane
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US1994/005464
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English (en)
Inventor
Charles R. Brent
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AU69511/94A priority Critical patent/AU6951194A/en
Publication of WO1994027031A1 publication Critical patent/WO1994027031A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/36—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movements defined in sub-groups F01C1/22 and F01C1/24
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder

Definitions

  • the system of the present invention relates to orbital rotary piston power systems, and to rotary vane mechanisms. More particularly the present invention relates to a power system for internal combustion engines, steam engines, fluid power units, fluid motors, pumps, compressors, turbochargers and the like, utilizing orbiting rotary vanes or rotary pistons confined within a close-fitting enclosure to provide expanding and contracting chambers that transmit power when coupled to input or output drive shafts.
  • Rotary piston pumps In the general field of powered pumps or engines, rotary piston pumps and rotary piston engines have been designed in many variations.
  • Rotary piston pumps are exemplified by the following U.S. patents: 4,373,484 issued to Boehling in 1983; 2,006,298 and 2,084,846 both issued to Hutchinson in 1935 and 1937 respectively; and earlier patents, 1,241,513 issued to Hicks in 1917, and 996,984 issued to Ginrod in 1911.
  • elliptical or elongated pistons rotate on shafts whose positions are fixed within a confined space.
  • the systems include rocker valves or ports positioned to admit fluids into an expanding chamber at its minimum volume or into a contracting chamber at or near its maximum volume, depending on whether expansion, pumping or compression was the desired power transmission effect.
  • rocker valves or ports positioned to admit fluids into an expanding chamber at its minimum volume or into a contracting chamber at or near its maximum volume, depending on whether expansion, pumping or compression was the desired power transmission effect.
  • Other such systems will also be referred to in the list of art that is included in applicant's art statement accompanying this application.
  • the , 484 patent to Boehling teaches an improved rotary piston mechanism including stationary components, and rotor components housed within the stator components.
  • the axles of the rotary components rotate within fixed positions in holes (or bearings) in the two stationary (stator) flat walls.
  • the present invention introduces a fluid mechanical power system for extracting energy from a working fluid such as steam, heated air and other gaseous or liquid fluids under pressure which produces work by expanding or pushing with force against moving parts within mechanically enclosed volumes, or, in an opposite mode of operation, imparting energy to a fluid when power is applied to a central shaft.
  • a working fluid such as steam, heated air and other gaseous or liquid fluids under pressure
  • an enclosed chamber housing a rotating hub plate, with the hub plate assembly supporting a plurality of spaced apart rotary vanes rotating on their own separate shafts and carried in a circular path by the hub plate assembly.
  • the rotation of the hub plate assembly imparts rotation to the plurality of vanes within the enclosed, tight-fitting chamber, the angular rotation of the vanes being some multiple or fractional multiple of, as depicted here one-half, the angular velocity at which the hub plate and power shaft are rotating and transmitting power.
  • the volume between the vanes increases and decreases, so that the volume of fluid within that space is contracted or expanded to drive the system or provide a source of power to the system or the working fluid.
  • the volume of fluid between the vanes is determined principally by the thickness of the vane when the vane is perpendicular to the end of its radius of travel on one side of this circular path and also determined by the width of the vane when it is aligned along the radius of travel, depicted here on the opposite side of the circular path.
  • the inherent volume ratio of the maximum volume between vanes to the minimum volume between vanes ranges from about two to one (2 : 1) for three vanes with mechanically sound dimensions (2.7: 1 as depicted herein) to about eight to one (8 : 1) for multiple vane units with more than four vanes.
  • This inherent volume expansion ratio can by multiplied by a factor of two(2) to ten(10) by appropriate limiting elements, such as slide valves, injector arrangements or superchargers, allowing the unit to function as a basic power unit for a Rankine cycle steam engine, an Otto cycle internal combustion engine, a Brayton cycle (hot) gas engine, a Sterling engine, or a Diesel engine burning fuel oils.
  • a Rankine cycle steam engine an Otto cycle internal combustion engine
  • a Brayton cycle (hot) gas engine a Sterling engine
  • Diesel engine burning fuel oils a Diesel engine burning fuel oils.
  • the volume expansion draws fluids into the chambers and the vanes impart motion to the fluid exiting the system by positive displacement of the fluids within the chambers.
  • FIGURE 1 is a vertical cross-sectional view of an embodiment of the mechanism of this invention as a pump taken in a plane perpendicular to the power shaft and showing a configuration of the orbiting, rotating members, one of which is in its top-dead-center position within a chamber of close-fitting confining walls;
  • FIGURE 2A is a vertical sectional view of the apparatus of the present invention along the axis of the power shaft with the basic power system utilized as a pump;
  • FIGURE 2B is a vertical sectional view of the apparatus of the present invention along the axis of the power shaft with the basic power system utilized as a steam engine;
  • FIGURE 3 is cross-sectional view illustrating schematically the interrelationship of stator, backplate and rotating members at different rotational positions within one complete rotation of the backplate and power shaft of the apparatus of the present invention
  • FIGURES 4A through 4F illustrate schematic views of the apparatus of the present invention during one third of a rotation cycle of the preferred embodiment of the present invention
  • FIGURES 5A and 5B illustrate partial views of the gearing mechanism interconnecting the power shaft with the rotating vanes in the preferred embodiment of the apparatus of the present invention
  • FIGURE 6 illustrates a schematic view of the apparatus of the present invention where there is a one to one gear ratio causing the vanes to span the chamber with two nodes.
  • FIGURES 1 through 5B would illustrate the preferred embodiment of the apparatus of the present invention by the numeral 10.
  • FIGURES 1 through 4F more particularly illustrate the apparatus of the present invention utilized as a pump in FIGURES 1 and 2A or as a steam engine in FIGURES 2B and 4A through 4F.
  • a principal cavity 14 which could be referred to as a stator cavity 14, with cavity 14 formed by a principal housing 16, with housing 16 formed by a continuous side wall 18, wherein there is defined the internal cavity 14 formed by the continuous side wall 18, the front portion 19 and the back 21.
  • side wall 18 is non- circular in configuration, but would have a uniform depth (D) as seen in FIGURES 2A and 2B, which would be in perpendicular conjunction with front wall 19 and back plate 31.
  • D depth
  • central member 24 which could be defined as a fixed stator 24, having a teardrop shape, with somewhat cylindrical, but not circular cylindrical walls 26, extending perpendicular from front wall 19 and further shaping the cavity 14.
  • a plurality of internal moving members, or vanes 34 which together with other essential components, constitute the mechanical power assembly constituting the present invention.
  • said cavity 14 is closed on the back by a rotating backplate 29 which is flat on its internal face 31 and circular on the edge 32.
  • the rotating backplate 29 is affixed to a drive shaft 33 which provides an output or input source of power.
  • a plurality of one or more identical rotating members or vanes 34 having a body portion 35, defining semi- cylindrical ends 42 and 44 and the two flat sides 38 and 39 therebetween, which are driven during operation.
  • Each of the vanes 34 is affixed to its own individual shaft 36 extending through the backplate 29, and, in high pressure applications, rotates on a circular plate 37.
  • the vanes are equally spaced apart in such a manner to divide the cavity 14 into a plurality of specific volume chambers 40 which vary in volume as the backplate 29 rotates and the vanes 34 move through the cavity 14, sealing off the chambers 40 formed between the wall 18 of the housing 16 and the central stator 24.
  • Precise means of positioning the rotating members or vanes 34 and imparting their rotation on the individual shafts 36 is done in such a manner that each vane 34 rotates at some exact multiple or fraction of the speed of the drive shaft 33 and backplate assembly 29, exactly one-half of the speed of the drive shaft as shown in FIGURES l through 5B.
  • FIGURE 6 illustrates a basic power unit with a one to one ratio of vane rotation to shaft rotation.
  • a central stationary gear 43 wherein passes the central shaft 33 without engagement, the central gear 43 is geared into reversing gears 46, which in turn impart rotation to the vane shafts 36 in gears 48.
  • the central gear 43, reverse gears 46 and the vane shaft gears 48 provide the 2:1 rotation ratio (as depicted here) between the central power shaft 33 and the vane shafts 36.
  • the rotating members or vanes 34 on the opposite side of the backplate 29 and all rotating members on shaft 36 opposite to the rotating members 34 may be held in place by two locking nuts 47, adjustable for timing purposes, or by other means.
  • FIGURES 3 and 4 the drawings which illustrate the theory of operation of the system during the cycles of rotation of the members previously referred to.
  • the backplate 29 which is flat and circular is rotating and sealing the cavity 14 and providing a circular orbit for the rotating vanes.
  • the vanes 34 positioned at a fixed distance from the center of the drive shaft 33 continually span the cavity 14 and close off or divide each chamber 40 of cavity 14 formed between each pair of vanes 34, from the other chambers, continuously varying the width and volume of each chamber 40 by their own rotation, allowing expanding or pressurized substances to expand or push against the rotating members, thus impelling the backplate 29, shaft 33 and rotor 34 assembly to turn and deliver power at the output shaft 33.
  • This means includes a slide or slide valve 50 positioned within the stator at or near the narrowest point in cavity 14.
  • slide valve 50 is lifted into a position intervening across cavity 14 by a cam 52 affixed to drive shaft 33, as the drive shaft 33 turns the back plate 29 into a position where a rotating member 34 has just cleared the end of slide valve 50.
  • An extension at the bottom of the slide valve 50 fits into a retracting groove 54 in backplate 29, thus retracting the slide valve 50 as the next rotating member 34 approaches.
  • the slide valve 50 limits the initial size of the cavity 40 which is initiating a power stroke, increasing the volume expansion ratio up to a nominal value of 22:1 (as shown here).
  • the chamber limiting slide valve 50 could equally as well be positioned to intervene from through the outer wall 18 of cavity 14, lowered by one or more springs and a cam built into the edge 32 of backplate 29 as illustrated in Figure 2B.
  • a mounting base 60 utilized as a pump or motor mount, is affixed or molded to the case 62 where appropriate to hold the motor or pump in a fixed position as desired.
  • FIGURES 3 and 4A through 4F depict a complete drive cycle in FIGURE 3 and an injection- partial expansion power cycle in FIGURES 4A-4F in the system of the present invention.
  • FIGURES 4A through 4F initially, as illustrated in FIGURE 4A, there is illustrated the steam engine format 12 with the cavity 14 formed within, between the housing wall 16, the wall of the stator 24, the front wall 19 and the rotating backplate 29.
  • vanes 34 positioned on the rotating backplate 29 within the system. It should be noted, as stated earlier, vanes 34 as shown here are rotating at one-half the speed of the backplate 29 in the cavity 14.
  • each pair of vanes would define a separate chamber 40, which chambers are depicted as chambers A, B, and C, along with chamber A' formed by the intervention of slide valve 50. Therefore, as illustrated, a volume of steam 100 being injected into the chamber A' would expand with force against the receding vane 34, moving it and making chambers A' and B slightly larger, and therefore it, along with the vane enclosing chamber B, which received its charge of steam just 120° prior to chamber A', impart rotation to the backplate 29, as seen in FIGURE 4C.
  • FIGURE 4D illustrates further expansion of the steam in chambers A' and B with additional steam being injected into A' if needed for maximum torque demands.
  • FIGURE 4E represents movement and expansion of chambers A' and B again, chamber B shown almost to full expansion in FIGURE 4F. Now the steam in chamber A', which has now become chamber A, expands through the same path and volume change as was just illustrated for chamber B until it reaches full expansion, thus ending one power expansion stroke for chamber A.
  • FIGURE 4A As was previously noted, the vane 34, which was in the position as noted in FIGURE 4A has since rotated from the top-dead-center position in FIGURE 4A to the position shown in FIGURE 4F, where a second vane 34 is moving into top- dead-center position from the position illustrated in FIGURE 4A. It is this sequence of events from FIGURE 4A through FIGURE 4F which will represent one repeating injection cycle sequence in the power cycle as the vanes are rotated throughout the chamber.
  • One complete power stroke for one chamber is represented by the movement of a single chamber through the expansion which both chambers A' and B have experienced as illustrated in FIGURES 4A through 4F, thus two power strokes and an exhaust stroke are occurring simultaneously in the three vane steam engine depicted in FIGURES 4A through 4F.
  • FIGURE 3 there is depicted a sequential view of three identical vanes 34 being rotated within the cavity 14 and the circular base under each of the vanes 34 representing the plate 37 upon which each of the vanes rotate as they are rotated by vane gears 48, as described earlier.
  • This sequential depiction shown in phantom view in FIGURE 3 of each of the vanes 34 illustrates clearly the type of rotation that a vane undergoes as a complete revolution is completed, i.e., each vane depicted here would undergo a one-half rotation as it rotates through one complete revolution of the backplate 29 and shaft 33.
  • FIGURE 6 is a similar view illustrating a power unit in which the vanes undergo one complete reverse rotation as the backplate-hub shaft assembly undergoes one complete rotation.
  • the charge of steam 100 expands with force against the receding vane, transmitting a smooth torque on the shaft through the connection of the vane shaft, backplate and hub assembly. Under normal operation the torque does not vary by a factor of more than two or three during 210 to 240 degrees of traverse of the vane during a power stroke, which places it at or near the exhaust port. While the aforementioned vane travels through its power stroke, a second vane trailing it by 120 degrees of revolution has likewise received its charge of steam and traversed almost half of the path of its power stroke.
  • the steam injector or a second steam injector could direct the full pressure of the steam from the boiler for the first 60 degrees of rotation or for the full traverse of the vane in its power stroke, providing much greater torque; providing of course that the motor components were designed to handle such a heavy load.
  • These maximum power conditions could only be achieved with considerable sacrifice of efficiency, because the engine would exhaust the steam out of the engine at 1/3 to 1/2 its maximum steam pressure, not a very efficient use of steam.
  • FIGURE 6 there is provided an embodiment of the apparatus 10 which would include a one to one gear ratio thus creating two nodes within chamber space 14, when the individual vanes 34 are rotated via shaft 33 around the stator member 24.
  • Different gear ratios can rotate the vanes 34 so that they span the chamber 14 with more than one node (maximum width) .
  • a one to one gear ratio spans the chamber 14 with two nodes, as seen in FIGURE 6, providing the basis for a balanced pump mechanism.
  • the thickness and strength of the rotating vanes 34, and any other members necessary can be changed to meet lesser or greater demands on the power unit or pumping system, as well as changing bearings, shaft size, sealing members, lubrication systems and the like to meet the demands of any particular application of the mechanical power system.
  • FIGURE 1 are required to transmit fluid smoothly through the pumping system.
  • the equations provided within this patent accept changes in thickness, radius of travel and length of the rotating members, readily generating the rotating members
  • XQ the X coordinate of the center of curvature of the outside tip of a vane 42
  • Y 0 the Y coordinate of the center of curvature of the outside tip of a vane 42
  • Xj the X coordinate of the center of curvature of the inside tip of a vane 44
  • Y ⁇ the Y coordinate of the center of curvature of the inside tip of a vane 44
  • Xc the X coordinate of the center of the drawing (or screen) or the center of the power drive shaft
  • R the radius of travel of the centers of the vanes
  • w the angle of travel of a vane from its top dead center position as it traverses the cavity, measured in radian.
  • L the length of the flat sides 38 and 39 of a vane from a frontal view without the added dimensions of its circular tips
  • RT the radius of curvature of the semi-circular cylindrical vane tips.
  • XOW,YOW the X,Y coordinates of points on the outer confining wall 18
  • XIW,YIW the X,Y coordinates of points on the inner confining wall 26
  • the shape of the confining cavity for the vane shape illustrated can be determined. Also the offset path of a milling tool whose center is travelling one tip radius from each wall can be determined by calculating enough points XO,YO and XI,YI to provide the required milling precision. Obviously other vane shapes can be employed in the rotary vane power system design.
  • apparatus 10 steam engine 12 principal cavity 14 principal housing 16 continuous side wall 18 front wall 19 back 21 depth D central stator member 24 central stator wall 26 backplate 29 internal face 31 side edge 32 central drive shaft 33 vanes 34 body portion 35 vane shafts 36 circular plate 37 flat sides 38, 39 ends 42, 44 chambers 40 chambers A, A', B, C stationary gear 43 reversing gear 46 vane gears 48 backside 45 locking nuts 47 slide or slide valve 50 cam 52 retracting groove 54 mounting base 60 motor case 62 steam injector 70 seals 72 charge of steam 100 passages P

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention concerne un système mécanique de transmission de puissance de base pour ailettes rotatives présentant une chambre dans laquelle est prévue une collerette de moyeu rotative (29) supportant une pluralité d'ailettes rotatives espacées (34) tournant sur leur axe propre et déplacée sur un chemin circulaire par celle-ci. La rotation de l'ensemble collerette de moyeu fait tourner la pluralité d'ailettes dans la chambre fermée, la rotation angulaire des ailettes correspondant à la moitié de la vitesse angulaire de rotation de la collerette de moyeu et de l'essieu moteur (33). Pendant la rotation des ailettes, le volume entre ces dernières augmente et diminue de manière à entraîner le système ou à envoyer une source d'énergie dans le système ou dans le fluide moteur.
PCT/US1994/005464 1993-05-13 1994-05-13 Systeme mecanique de transmission de puissance pour ailettes rotatives Ceased WO1994027031A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU69511/94A AU6951194A (en) 1993-05-13 1994-05-13 Rotary vane mechanical power system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US08/061,199 1993-05-13
US08/061,199 US5375987A (en) 1993-05-13 1993-05-13 Rotary vane mechanical power system utilizing positive displacement

Publications (1)

Publication Number Publication Date
WO1994027031A1 true WO1994027031A1 (fr) 1994-11-24

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ID=22034278

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1994/005464 Ceased WO1994027031A1 (fr) 1993-05-13 1994-05-13 Systeme mecanique de transmission de puissance pour ailettes rotatives

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US (1) US5375987A (fr)
AU (1) AU6951194A (fr)
CA (1) CA2162678A1 (fr)
WO (1) WO1994027031A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005056182A1 (de) * 2005-11-18 2007-05-31 Reinald Ramm Turbine zum Erzeugen von Wellenenergie unter Verwendung des Tornadoprinzips
US8567178B2 (en) 2007-03-05 2013-10-29 Roy J. HARTFIELD, JR. Positive displacement rotary vane engine
WO2019068273A3 (fr) * 2017-10-03 2019-06-06 Korcak David Compresseur

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6533557B1 (en) * 2000-08-11 2003-03-18 David G. Williams Positive displacement pump
AU2003210463B2 (en) 2002-01-09 2008-02-14 Karnes Dyno-Rev Engine, Inc. Internal combustion engine
FR2870883A1 (fr) * 2004-05-28 2005-12-02 Vimak Soc Civ Ile Turbomachines a aubes rotatives
US20080135013A1 (en) * 2006-11-09 2008-06-12 Abdalla Aref Adel-Gary Paddling blades engine
US8079343B2 (en) * 2007-09-17 2011-12-20 John Howard Seagrave Positive-displacement turbine engine
DE102008047050A1 (de) * 2008-09-13 2010-04-01 Gößling, Werner, Dipl.-Ing. Rotationskolben Wasserkraftmaschine
US8480444B2 (en) * 2009-10-15 2013-07-09 Tracker Marine, L.L.C. Rotary engine jet boat
EP2690251B8 (fr) * 2011-03-23 2016-12-14 Takeshi Ishii Turboréacteur de fusée à 3 temps/à 6 temps
MX2024009175A (es) * 2022-01-28 2024-09-10 Milan SEVCIK Turbina de palas giratorias.

Citations (5)

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Publication number Priority date Publication date Assignee Title
US1136976A (en) * 1905-03-02 1915-04-27 Frank Reaugh Pump or motor.
US1394861A (en) * 1919-08-26 1921-10-25 Reaugh Frank Pump or motor
DE883563C (de) * 1951-04-28 1953-08-03 Karl Rabe Dr Med Drehkolbenmaschine mit drehbaren Verdraengerschaufeln
US3636930A (en) * 1969-03-28 1972-01-25 Fukumatsu Okada Rotary engine
US4055156A (en) * 1976-03-12 1977-10-25 Gundlach, S.A. Rotary engine

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US996984A (en) * 1907-08-30 1911-07-04 John Grindrod Pump.
US1241513A (en) * 1917-02-07 1917-10-02 George C Hicks Jr Pump.
US2006298A (en) * 1933-04-21 1935-06-25 Multicycol Pump & Engine Corp Rotary pump compressor, engine, and the like
US2084846A (en) * 1934-10-26 1937-06-22 Multicycol Pump & Engine Corp Rotary pump, compressor, engine, and the like
GB988161A (en) * 1961-07-26 1965-04-07 Rota Societa Meccanica Italian Improvements in or relating to rotary internal combustion engines
US3302870A (en) * 1966-02-25 1967-02-07 Gen Motors Corp Rotary compressor
NL168908C (nl) * 1975-08-05 1982-05-17 Herstal Sa Verbrandingsmotor met roterende zuigers en een centrale drukkamer.
US4373484A (en) * 1980-10-06 1983-02-15 Boehling Daniel E Rotary piston mechanism

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1136976A (en) * 1905-03-02 1915-04-27 Frank Reaugh Pump or motor.
US1394861A (en) * 1919-08-26 1921-10-25 Reaugh Frank Pump or motor
DE883563C (de) * 1951-04-28 1953-08-03 Karl Rabe Dr Med Drehkolbenmaschine mit drehbaren Verdraengerschaufeln
US3636930A (en) * 1969-03-28 1972-01-25 Fukumatsu Okada Rotary engine
US4055156A (en) * 1976-03-12 1977-10-25 Gundlach, S.A. Rotary engine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005056182A1 (de) * 2005-11-18 2007-05-31 Reinald Ramm Turbine zum Erzeugen von Wellenenergie unter Verwendung des Tornadoprinzips
DE102005056182B4 (de) * 2005-11-18 2008-01-24 Reinald Ramm Verfahren und Anordnung zum Erzeugen von Energie an einer Antriebswelle (Tornadoturbine)
US8567178B2 (en) 2007-03-05 2013-10-29 Roy J. HARTFIELD, JR. Positive displacement rotary vane engine
WO2019068273A3 (fr) * 2017-10-03 2019-06-06 Korcak David Compresseur

Also Published As

Publication number Publication date
AU6951194A (en) 1994-12-12
CA2162678A1 (fr) 1994-11-24
US5375987A (en) 1994-12-27

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